CN109891116B - Damping valve for shock absorber - Google Patents
Damping valve for shock absorber Download PDFInfo
- Publication number
- CN109891116B CN109891116B CN201780067576.1A CN201780067576A CN109891116B CN 109891116 B CN109891116 B CN 109891116B CN 201780067576 A CN201780067576 A CN 201780067576A CN 109891116 B CN109891116 B CN 109891116B
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- Prior art keywords
- star
- spring
- valve according
- damper valve
- springs
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
- F16F9/3488—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by features intended to affect valve bias or pre-stress
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F1/00—Springs
- F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
- F16F1/32—Belleville-type springs
- F16F1/324—Belleville-type springs characterised by having tongues or arms directed in a generally radial direction, i.e. diaphragm-type springs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
- F16F9/3485—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by features of supporting elements intended to guide or limit the movement of the annular discs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/042—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with locking or disconnecting arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/044—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with more than one spring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2226/00—Manufacturing; Treatments
- F16F2226/04—Assembly or fixing methods; methods to form or fashion parts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2226/00—Manufacturing; Treatments
- F16F2226/04—Assembly or fixing methods; methods to form or fashion parts
- F16F2226/042—Gluing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2226/00—Manufacturing; Treatments
- F16F2226/04—Assembly or fixing methods; methods to form or fashion parts
- F16F2226/048—Welding
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Springs (AREA)
- Fluid-Damping Devices (AREA)
Abstract
Damping valve (1) comprising a damping valve body (3) having at least one through-channel (7) whose outlet cross-section (23) is at least partially covered by at least one valve disk (13), wherein the at least one valve disk is pretensioned by at least two star springs (31, 33, 35), wherein each star spring has a bearing ring (37, 39, 41) and a plurality of radial spring arms (45), wherein the bearing rings are stacked on one another in a mounted position, wherein the star springs are arranged in a congruent manner such that the spring arms of at least two adjacent star springs point in the same direction relative to the valve disk, and wherein the star spring group has a torsion stop element (53, 59, 61, 69, 71, 73) in an assembled position.
Description
Technical Field
The present invention relates to a damping valve for a shock absorber according to the preamble of claim 1.
Background
DE 761446B discloses a damping valve having a damping valve body with a through-passage whose outlet cross section is at least partially covered by a valve disk. The star spring causes the necessary closing force of the valve disk, which is supported on the support disk to limit the lifting movement of the valve disk. The star spring has a support ring with a plurality of spring arms extending radially outward from the support ring. The spring arms are not connected to each other except for the support ring, so that each spring arm can be deformed independently of the adjacent spring arm.
Between the spring arms, a free space extends, which forms in particular a flow path for further through-channels having an opposite flow direction. The free space has a larger cross section in the circumferential direction than the spring arms.
DE 2353402 a1 discloses a damping valve in which a star spring is likewise used in the embodiment according to fig. 4 and 5. The star springs with the basic design according to DE 761446B are arranged in opposite layers, i.e. the bearing rings are in contact, and the spring arms extend with their bearing rings facing each other.
In principle, the star spring offers the advantage that an asymmetrical closing force can be applied to the valve disk. Although in principle it is also possible to achieve a greater closing force, the life of the star spring is significantly reduced as a result.
Disclosure of Invention
The aim of the invention is to reduce the problem of life limitation in the case of higher loading of the star spring.
This object is achieved thereby: the star springs are stacked in the same direction, so that the spring arms of at least two adjacent star springs point in the same direction relative to the valve disk, and the star spring package has a rotation-blocking element in the assembled position.
The advantage of the invention is that, since instead of a single star spring, a plurality of individual weaker star springs are now used, they are significantly less critical in terms of life. However, in order to precisely concentrate the tension of the individual star springs and not to have the spring arms mounted without pretension or with reduced pretension, a torsion-blocking element is used which leads to a stacked arrangement of the spring arms. The stack arrangement must only be maintained during transport from the material silo until the loading of the completed damper valve. In the case of a completely assembled damper valve, the friction force keeps the spring arms in a stacked arrangement even if the torsion stop element is no longer active.
In one embodiment, the rotation-blocking element is formed by at least one weld. In principle, spring steel may be more difficult to weld than structural steel, however the load on the stack during assembly is very small.
It has proven to be particularly advantageous if the weld is embodied as a resistance weld. The resistance welding portion can realize a short tact time and a simple structure.
In order to also be able to weld a plurality of star springs to one another precisely, the star springs have at least one access opening, which is at least partially covered by an adjacent star spring with a carrier section. Therefore, two adjacent spider springs are always welded to each other. If more than two star springs are used in the stack, the star springs then have a plurality of access openings which are arranged in a defined angular position with respect to the spring arms. In this case, the carrier section can be brought into register with the plurality of access openings very easily by means of the pivoted mounting position, and thus it is also ensured that the welding tool can approach both carrier sections in the middle of the stack and only then weld them to one another in a targeted manner.
Alternatively, the weld can be embodied as a laser weld, which is very advantageous in particular in terms of the introduction of heat into the star spring.
With regard to the fastening in the low-stress region of the star spring, the torsion-blocking element outside the spring arm establishes a connection with the bearing ring.
Additionally, the bearing ring can have at least one radial projection for arranging the rotation-blocking element. The radial protrusion does not actually change the spring characteristics of the spider spring.
For example, in the event that a suitable welding technique cannot be provided, the rotation-blocking element can also be formed by a securing bolt which projects beyond the bearing ring.
In principle, the rotation-blocking element can also be formed by a fixing sleeve, which forms an interference connection with the bearing ring, for example.
It is therefore possible for the fixing sleeve to act on the support ring on the inside. Even if the fixing sleeve projects slightly axially beyond the stack of bearing rings, there is still no functional disadvantage, since the installation space for the stack provides sufficient free space for this purpose.
Alternatively, the fixing sleeve can also act on the support ring on the outside and have a recess for accommodating the spring arm. For example, an annular base can be provided, which has an axial projection which then engages into the free space between the spring arms of the star spring.
Depending on the size and material properties of the star spring, it can also be provided that the bearing rings are connected to one another by means of a snap connection. The snap-in engagement need not have a locking head. The radial pressing-in on a small cross section is sufficient to fix the spider springs to one another for the assembly process.
In principle, it is also possible to adhesively bond the support rings to one another. This variant requires particularly low expenditure.
Drawings
The invention is further elucidated with the aid of the following description of the figures. Wherein:
FIG. 1 shows a damping valve in a sectional illustration;
FIG. 2 shows a top view of the spider spring;
figures 3 and 4 show details of the spider spring set;
FIG. 5 shows a spider spring pack with a dead bolt;
FIGS. 6 and 7 show a spider spring pack with a fixed sleeve;
FIG. 8 shows a spider spring pack having a bite joint;
FIG. 9 shows a spider spring pack with laser welds;
fig. 10 shows a star spring package with an adhesive connection.
Detailed Description
Fig. 1 shows a damping valve 1 in the form of a piston valve. In principle, however, the invention is not limited to this form of construction. The damping valve 1 comprises a damping valve body 3 which has at least one through-channel 7 at the piston rod 5 which can connect a working chamber 9 remote from the piston rod with a working chamber 11 on the piston rod side. The outlet cross section of the at least one through-channel 7 is at least partially covered by a valve disk 13. For this purpose, the plurality of through-channels 7 open into an annular groove 15, which is delimited by a valve seat inner face 17, a valve seat outer face 19 and also forms an outlet cross section.
On a sub-circle radially inward with respect to the inner face 17 of the valve seat are further through-passages 21 for the flow from the working chamber 11 on the piston rod side to the working chamber 9 remote from the piston rod. The through-channel 21 likewise opens into an annular groove 23 on the bottom side of the damping valve body 3 and is covered by a second valve disk 25, which is prestressed in the closing direction by a helical spring 27. In principle, other spring types can also be used.
The valve disk 13 on the upper side of the damping valve body 3 has a through-opening 29 which opens into the through-passage 21. The star springs 31, 33, 35 are prestressed in the closing direction of the valve disk 13, and they abut with their inner bearing rings 37, 39, 41 against a bearing disk 43. All the support rings 37, 39, 41 are stacked and pressed between the damping valve body 3 with the valve disk 13 and the support disk 43.
Fig. 2 shows a plan view of the star springs 31, 33, 35. Each spider spring 31, 33, 35 has a bearing ring 37, 39, 41 from which a plurality of spring arms 45 extend radially. In fig. 2, the spring arms 45 extend radially outward. The invention also contemplates an outer support ring and radially inwardly directed spring arms.
Within the limits of manufacturing tolerances, all spring arms 45, 47, 49 are stacked with maximum overlap, wherein, as shown in fig. 1, all spring arms 45, 47, 49 of at least two adjacent star springs point in the same direction relative to valve disk 13. Additionally, with reference to fig. 3, the respective spring arms 45, 47, 49 of the laminated star springs 31, 33, 35 can be clearly seen therein.
The star spring arrangement according to fig. 1 to 3 has a rotation-blocking element in the assembled position, i.e. corresponding to fig. 3, which causes the angular orientation of all spring arms 45, 47, 49 to also coincide. It should be avoided that the star spring is mounted in a torsional manner with respect to the adjacent star spring and thus its spring arms engage in the free space 51 between two spring arms of the adjacent star spring.
In the embodiment according to fig. 2 and 3, the rotation-blocking element is formed by a weld 53 in the resistance-welded embodiment. Between two adjacent spring arms and thus beyond the spring arms, each bearing ring 37, 39, 41 has a radial projection 55 at its outer diameter for the arrangement of a rotation-blocking element 53. In this case, one of the radial projections has an access 57, which is at least partially closed by the adjacent star spring 33 with its bearing ring 39.
Fig. 2 shows a star spring 31, 33, 35 with six radial projections 55. If star springs differing in material size are used, then the star springs 31, 35 on the surface side can each be provided with an access 57, and the middle star spring 33 is embodied without an access. Thus, two adjacent star springs can be welded to one another without problems, wherein the access facilitates the contact between the electrode and the central star spring 33 (see fig. 4)
If more than three star springs of the same type are welded, it is proposed here that a respective radial projection 55 of the star springs is embodied without an access 57 and the other projections 55 are embodied with accesses 57. When the star springs are stacked in groups, two adjacent star springs are aligned with their inlets 57 in accordance with one another. Therefore, the projections 55 without the access ports 57 coincide in the axial direction, and can thus be easily welded.
The subsequent star spring pair is assembled in an offset manner to one spring arm, but with the same orientation of the inlet as the first star spring pair. The welding tool can thus be guided by the existing access openings of the star springs above and below it to the star spring pair in the middle thereof, in order to weld them at their radial projection without access opening.
In fig. 5, all radial projections 55 have an access 57, through which a securing bolt 59 penetrates the bearing rings 37, 39, 41 as a rotation-blocking element. However, in this variant, a radial projection may not necessarily be necessary. In principle, the radial projections 55 serve to provide a radial cross section which unloads the bearing ring. In the corresponding support ring cross-section, the pronounced radial projection 55 can be dispensed with.
It has been found that the respective torsion stop element 57 can exert a sufficiently large holding force in order to hold the star spring package together during the assembly process.
Fig. 6 shows a section through the star spring package 31, 33, 35 with a fixing sleeve 61 as a rotation-blocking element, which acts on the inside on the bearing rings 37, 39, 41 and forms an interference fit therewith. When assembled, the individual star springs 31, 33, 35 are aligned with one another in the circumferential direction and then introduced into the fixing sleeve 61. The fixing sleeve may protrude beyond the spider spring pack. A small free space for accommodating the projecting sleeve volume can be provided in the support disk.
Fig. 7 shows that the fixing sleeve 61 can also act on the support rings 37, 39, 41 on the outside in such a way that it has a recess 63 for accommodating the spring arms 45, 47, 49. The fixing sleeve 61 has a base 65, as well as the planar extension of the support rings 37, 39, 41. Starting from this base, retaining webs 67 extend, which engage between the spring arms 45, 47, 49 and with their inner walls abut the edges of the bearing rings 37, 39, 41.
Fig. 8 shows a further variant in which the bearing rings are connected to one another by a rotation-blocking element in the form of a snap connection 69. The snap-in connection does not have to be embodied such that a complete locking head is present. The press fit between the regions of the bearing rings 37, 39, 41 that engage into one another is sufficient to achieve the required holding force.
In a further embodiment according to fig. 9, the rotation-blocking element is formed by a laser weld 71, which is preferably implemented at the outer edge region of the bearing rings 37, 39, 41, since access for welding tools is particularly simple here. The laser weld 71 exhibits a particularly low thermal load and can therefore also be used particularly well in the case of very thin walls of the spider springs 31, 33, 35.
In principle, it is also possible according to fig. 10 to bond the bearing rings 37, 39, 41 of the star springs 31, 33, 35 to one another by means of an adhesive layer 73 between the star springs 31, 33, 35, so that the adhesive layer forms a rotation-blocking element. Due to the low requirements, simple adhesive techniques can also be used, since, as already mentioned, the durability of the adhesive connection is not necessary.
List of reference numerals
1 damping valve
3 damping valve body
5 piston rod
7 through channel
9 working chamber far away from piston rod
11 working chamber on the piston rod side
13 valve disk
15 annular groove
17 inner face of valve seat
19 outside the valve seat
21 through passage
23 annular groove
25 valve disk
27 helical spring
29 cross section through
31 control spring
33 control spring
35 control spring
37 support ring
39 supporting ring
41 supporting ring
43 support disc
45 spring arm
47 spring arm
49 spring arm
51 free space
53 weld
55 radial projection
57 connecting port
59 fixing bolt
61 fixed sleeve
63 recess
65 bottom
67 holding tab
69 bite joint
71 laser welding part
73 adhesive layer
Claims (12)
1. A damper valve (1) comprising a damper valve body (3) having at least one through-channel (7) whose outlet cross-section (23) is at least partially covered by at least one valve disk (13), wherein the at least one valve disk (13) is prestressed by at least two star springs (31, 33, 35), wherein each star spring (31, 33, 35) has a support ring (37, 39, 41) and a plurality of radial spring arms (45), wherein the support rings (37, 39, 41) are stacked on one another in a mounted position, characterized in that the star springs (31, 33, 35) are stacked in the same direction, such that the spring arms (45) of at least two adjacent star springs point in the same direction relative to the valve disk (13), and in that the star spring group has a torsion stop element (53, 53) in the mounted position, 59. 61, 69, 71, 73), the rotation-blocking element (53, 59, 61, 69, 71, 73) being connected to the bearing ring (37, 39, 41) outside the spring arms (45), the rotation-blocking element holding each two adjacent star springs together before the complete damper valve is installed, so that a star spring group is formed.
2. The damper valve according to claim 1, characterized in that the torsion stop element is formed by at least one weld (53).
3. The damper valve according to claim 2, wherein the welded portion (53) is a resistance welded portion.
4. Damping valve according to claim 1, characterized in that the star spring (31, 33, 35) has at least one access (57) which is at least partially covered by an adjacent star spring (31, 33, 35) with a support ring (37, 39, 41).
5. The damper valve according to claim 2, characterized in that the weld (53) is a laser weld (71).
6. The damper valve according to claim 4, characterized in that the bearing ring (37, 39, 41) has at least one radial projection (55) for arranging the torsion stop element (53).
7. The damper valve according to claim 1, characterized in that the torsion stop element is formed by a securing bolt (59) which is clamped over the bearing ring (37, 39, 41).
8. The damper valve according to claim 1, characterized in that the torsion stop element is formed by a fixing sleeve (61).
9. The damper valve according to claim 8, characterized in that the fixing sleeve (61) acts on the support ring (37, 39, 41) on the inside.
10. The damping valve according to claim 8, characterized in that the fixing sleeve (61) acts on the support ring (37, 39, 41) on the outside and has a recess (63) for accommodating the spring arm (45).
11. The damper valve according to claim 1, characterized in that the support rings (37, 39, 41) are connected to one another by means of a snap-in joint (69).
12. Damping valve according to claim 1, characterized in that the support rings (37, 39, 41) are glued to each other.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102016221659.7A DE102016221659B4 (en) | 2016-11-04 | 2016-11-04 | Damping valve for a vibration damper |
DE102016221659.7 | 2016-11-04 | ||
PCT/EP2017/075098 WO2018082852A1 (en) | 2016-11-04 | 2017-10-04 | Damping valve for a vibration damper |
Publications (2)
Publication Number | Publication Date |
---|---|
CN109891116A CN109891116A (en) | 2019-06-14 |
CN109891116B true CN109891116B (en) | 2021-09-28 |
Family
ID=60043178
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
CN201780067576.1A Active CN109891116B (en) | 2016-11-04 | 2017-10-04 | Damping valve for shock absorber |
Country Status (5)
Country | Link |
---|---|
US (1) | US11098781B2 (en) |
KR (1) | KR20190080910A (en) |
CN (1) | CN109891116B (en) |
DE (1) | DE102016221659B4 (en) |
WO (1) | WO2018082852A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017221122B4 (en) * | 2017-11-27 | 2021-03-18 | Zf Friedrichshafen Ag | Damping valve for a vibration damper |
EP3832158A4 (en) * | 2018-07-31 | 2022-03-16 | Showa Corporation | Valve mechanism and shock absorber |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE970515C (en) * | 1950-06-13 | 1958-09-25 | Christian M L L Bourcier De Ca | Shock absorber pistons for land vehicles |
US3001419A (en) * | 1960-04-29 | 1961-09-26 | Hymans Harold | Oscillation or inertia damper |
DE3906128A1 (en) * | 1989-02-28 | 1990-08-30 | Krebsoege Gmbh Sintermetall | Valve for oscillation dampers, particularly motor-vehicle shock absorbers |
CN1499101A (en) * | 2002-10-31 | 2004-05-26 | �泡��ҵ��ʽ���� | Damp force generating valve of hydraulic damper |
DE102009054121A1 (en) * | 2009-11-20 | 2011-05-26 | Volkswagen Ag | damper valve |
CN103790960A (en) * | 2012-10-31 | 2014-05-14 | 安维斯德国有限责任公司 | Spring functional component for a hydroelastic bearing and hydroelastic bearing |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE761446C (en) | 1937-07-29 | 1952-11-04 | Gen Motors Corp | Fluid damper with progressive damping for motor vehicles |
US2648405A (en) * | 1949-12-17 | 1953-08-11 | Patent Dev Company | Piston assembly for shock absorbers |
US2699844A (en) * | 1950-03-14 | 1955-01-18 | Patent Dev Company | Shock absorber construction |
US2676676A (en) * | 1950-03-22 | 1954-04-27 | Houdaille Hershey Corp | Telescopic shock absorber |
DE2353402A1 (en) | 1973-10-25 | 1975-05-07 | Fichtel & Sachs Ag | Spring loaded valve-plates for shock absorbers - has inner piston apertures to permit high flow of fluid with small axial movement |
DE3001419A1 (en) | 1980-01-16 | 1981-07-23 | Hans 8202 Bad Aibling Ribbert | Injecting earth or rock - involves forcing material out by relatively moving pistons, pref. in driven lance |
GB2226620B (en) * | 1988-10-25 | 1992-11-04 | Tokico Ltd | Hydraulic damper |
DE19524948A1 (en) * | 1994-07-30 | 1996-02-01 | Volkswagen Ag | Automotive exhaust vibration damper |
DE19731138C2 (en) * | 1997-07-21 | 2002-06-13 | Zf Sachs Ag | Damping force adjustable vibration damper |
DE102009043572A1 (en) * | 2009-09-30 | 2011-04-14 | Häussermann Lamellen GmbH | Disk spring arrangement for use in spring assembly, has spring ring, which has radial outer circumferential support edge on inner surface for supporting on support surface |
DE102010062324B4 (en) | 2010-12-02 | 2015-01-29 | Zf Friedrichshafen Ag | Damping valve arrangement for a vibration damper |
-
2016
- 2016-11-04 DE DE102016221659.7A patent/DE102016221659B4/en active Active
-
2017
- 2017-10-04 WO PCT/EP2017/075098 patent/WO2018082852A1/en active Application Filing
- 2017-10-04 CN CN201780067576.1A patent/CN109891116B/en active Active
- 2017-10-04 US US16/346,966 patent/US11098781B2/en active Active
- 2017-10-04 KR KR1020197015561A patent/KR20190080910A/en not_active Application Discontinuation
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE970515C (en) * | 1950-06-13 | 1958-09-25 | Christian M L L Bourcier De Ca | Shock absorber pistons for land vehicles |
US3001419A (en) * | 1960-04-29 | 1961-09-26 | Hymans Harold | Oscillation or inertia damper |
DE3906128A1 (en) * | 1989-02-28 | 1990-08-30 | Krebsoege Gmbh Sintermetall | Valve for oscillation dampers, particularly motor-vehicle shock absorbers |
CN1499101A (en) * | 2002-10-31 | 2004-05-26 | �泡��ҵ��ʽ���� | Damp force generating valve of hydraulic damper |
DE102009054121A1 (en) * | 2009-11-20 | 2011-05-26 | Volkswagen Ag | damper valve |
CN103790960A (en) * | 2012-10-31 | 2014-05-14 | 安维斯德国有限责任公司 | Spring functional component for a hydroelastic bearing and hydroelastic bearing |
Also Published As
Publication number | Publication date |
---|---|
US11098781B2 (en) | 2021-08-24 |
CN109891116A (en) | 2019-06-14 |
DE102016221659B4 (en) | 2022-07-07 |
US20200063818A1 (en) | 2020-02-27 |
KR20190080910A (en) | 2019-07-08 |
WO2018082852A1 (en) | 2018-05-11 |
DE102016221659A1 (en) | 2018-05-09 |
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